Bearing

ABSTRACT

A bearing, joint or knuckle, e.g. between a steering rod and a lever or arm connected to a wheel in an automotive stearing linkage, is provided with an inner and/or an outer metal shell or sleeve to which a rubber layer is vulcanized, the force being transmitted between the inner surface and the outer surface of the joint through elastic deformation of the elastomeric layer. One or both of the shells is, according to the invention, slotted parallel to generatrices of the shell.

United States Patent [191 J iirn et al.

[ Dec. 25, 1973 [22] Filed:

[ BEARING [75] Inventors: Raoul Jiirn, l-lengnau; Peter Reichardt,Fellbach, both of 1 Germany [73] Assignee: Raoul Jorn, Hengau, PostWasserburgh A.B., Germany Feb. 22, 1972 211 Appl. No.: 228,153

[30] Foreign Application Priority Data Feb. 20, 1971 Germany P 21 08154.9

Sept. 6, 1971 Germany P 21 44 507.8

[52] US. Cl. 308/238, 287/85 R, 308/26 [51] Int. Cl. F16c 33/04 [58]Field of Search ..L 308/238, 26; 287/85 R [56] References Cited UNITEDSTATES PATENTS 3,368,852 2/1968 l-lerbenar et al 308/26 3,494,676 2/1970Compton 308/238 3,108,830 10/1963 Fierstine.... 308/238 3,130,991 4/1964Piragino..... 308/238 2,797,929 7/1957 Herbenar 287/85 R 2,940,7856/1960 l-laushalter 287/85 R 3,096,128 7/1963 Wight 308/238 3,112,12311/1963 True 308/238 Primary Examiner-Charles J. Myhre AssistantExaminer-Barry Grossman AttameyKarl F. Ross [5 7 ABSTRACT A bearing,joint or knuckle, e.g. between a steering rod and a lever or armconnected to a wheel in an automotive stearing linkage, is provided withan inner and/or an outer metal shell or sleeve to which a rubber layeris vulcanized, the force being transmitted between the inner surface-andthe outer surface of the joint through elastic deformation of theelastomeric layer. One or both of the shells is, according to theinvention, slotted parallel to generatrices of the shell.

60 Claims, 24 Drawing Figures PATENTEU DEC 25 I975 SHEET EM 3 mt 6E .x

PATENTED DEC 25 I973 SHEET 30F 3 BEARING CROSS-REFERENCE TO RELATEDAPPLICATIONS This application is related to application Ser. No. 86,167filed 2 November 1970 (now U.S. Pat. No. 3,666,301) and entitled PIVOT RSUPPORT SLEEVE WITH RESILIENT LAYER, the applicant being Raoul Jorn, theassigneeof the instant case and a coinventor of the subject matterthereof.

FIELD OF THE INVENTION BACKGROUND OF THE INVENTION It has been proposed,in the above-identified application and elsewhere, to provideelastomeric layers between relatively movable parts to serve asvibration or shock dampers and/or to transmit force (e.g. a torque)between the two parts. For the most part, a metal layer is applied toone surface of an elastomeric sleeve while a second metallic layer orshell is applied to the other periphery. When the resulting spring isused as a vibration or shock-damping member, the outer shell is securedto one body while the inner shell is secured to the other. When thebodies are angularly displaceable about the axis of the composite springthus resulting, torque may be transferred by the elastomeric layer. Ingeneral, force is transmitted to the elastomeric layer by distortion ofthe layer within the elastic limit, upon a shell-type displacement ofone surface to bring about an equivalent displacement of the other.

It is important, inall such elastomeric pivot bearings to ensure acontinuous and unoffset relationship between an inner or outer metalsleeve and the elastomer layer bonded thereto. In other words, arelative frictional shifting of the metal sleeve and the adjacentelastomer layer must be precluded, without, however, materiallypreventing shear forces from elastically defonning the elastomericlayer. On the other hand, it has been a problem in conventional systemsto prevent radial distortion of the sleeve and the entire assembly, suchdistortion preventing the pivot from rotating properly within thebearing. Another important characteristic of composite bearingarrangements of this character is that the elastomer layer must beprestressed (i.e. precompressed) in the appropriate direction to resistthe shear forces mentioned above.

In cylindrical pivot bearings and sheeves, e.g. for automotive-vehiclesteering systems, it has been proposed to provide a highly precompressedrubber layer or ring between an inner slotted sleeve and an outerslotted sleeve, the sleeves bearing against the elastomer layer underfriction. Such pivot arrangements are expensive and the systems formounting same are complicated and difficult. During removal, it is notalways possible to prevent distortion so that reuse is often impossible.

The composite sleeves in elastomer assemblies, according to the presentinvention, are particularly intended for use as steering-knuckle pivotsin automotive-vehicle systems, pivot arrangements between the tie rodand the steering-knuckle arms, the pivot between the drag link and thesteering-knuckle arms or tie rod, the pivot between the pitman arm andthe drag links, the pivot between an intermediate knuckle arm and achassis member and the pivots between the intermediate knuckle arms,drag link and tie rods. In other words, wherever a pivot arrangement,ball joint, knuckle or the like may be used in an automotivevehiclesteering system or like arrangement and some relative angular movementand lateral axial or other further mobility, within arelatively limitedrange, is desired, the system described below may be employed.

OBJECTS OF THE INVENTION It is the principal object of the presentinvention to provide a sleeve-type junction arrangement of the characterdescribed which will avoid the above-mentioned disadvantages and tofurther the principles of the com monly assigned application mentionedearlier.

Yet another object of the invention is to provide an improved ball jointor like pivot arrangement for an automotive steering linkage.

SUMMARY OF THE INVENTION These objects and others which will becomeapparent hereinafter are attained, in accordance with the presentinvention, in a ball joint or other pivot joint, particularly for anautomotive-vehicle steering system wherein the transverse yielding ofthe elastomer layer at its outer and inner diameters, because of arelative shifting of this layer with respect to the inner and outermetal parts, is positively prevented and the elastomer layer is heldunder radial compression (prestress) in a simple and convenient mannerwhereby the pivot can be easily inserted and removed so that only acoarse fitting is required.An important characteristic of the inventionis also that the elastomeric pivot assembly may be used for relativelysmall parts of the steering linkage and is, in turn, of small size andcapable of being used in simple and lightweight structure.

These advantages are gained in a steering-linkage pivot consisting of agenerally tubular or hollow elastomer layer having at least oneperipheral metal sleeve running from one axial end face to the otheraxial end face and provided with longitudinal slits terminating at bothend faces and distributed in angularly spaced relationship about themetal sleeve. In other words, one or both of the metal sleeves isprovided with longitudinally extending slits or slots running from oneend face of the assembly until the opposing end face thereof. In thismanner, the transverse yielding of the elastomer at the interface atwhich the elastomer ring is bonded to the metal sleeve, is limited in anunobjectionable manner.

According to a more important feature of the present invention, theelastomeric ring is vulcanized to a sheetmetal sleeve or shell havingthe configuration of a surface of rotation defined by rotating ageneratrix about the axis of the pivot assembly and provided withelongated windows along generatrices and in angularly spacedrelationship such that the windows extend in the axial direction, i.e.along the respective generatrix over the major portion of the length ofthe sleeve or shell along this generatrix. In other words, at least 50percent and preferably percent or more of the length of the generatrixis constituted by one or more elongated openings collectively defining awindow and hereinafter referred to as a relatively wide slot. We havefound it to be advantageous to terminate the relatively wide slot, atone longitudinal end thereof, in the form of a narrow slot running tothe edge of the sheetmetal strip or member which is to be rolled to formthe shell or sleeve. Advantageously, a web of sheet metal, preferablyhaving a length along the generatrix which is a minor fraction of thegeneratrix length and the window or opening length which holds the striptogether and may be located at the end of the slot opposite that of thenarrow portion or at an intermediate location along the windowsubdividing it into a plurality of openings. It has been found to beadvantageous, moreover, to permit the elastomeric material to passthrough the windows and to form at least a thin elastomer film on theside of the sheet-metal shell opposite the main body of the elastomericmaterial. The elastomeric material can then be vulcanized to both broadsurfaces of the sheet-metal shell.

The system described above, wherein the shell and the elastomeric bodysurrounding it or surrounded by it, may have a cylindrical,frustoconical or generally spheroidal shape, or a shape which is ahybrid thereof, has numerous advantages. Firstly, the relativefrictional shifting of the elastomeric body and the, or each, metalsheeve or shell is precluded and the useful life of the assemblyincreased. The bearing or pivot member is radially expandable uponinsertion of a pin or stud of a larger diameter than the nominaldiameter of the assembly and, upon insertion of the assembly in asurrounding inelastic bushing, the insertion ofa larger stud may sufficeto provide the desired degree of precompression. Of course, in additionto being radially expandible, the assembly has a certain degree ofcontractibility and the precompression can be provided by inserting astud or stud shaft of a diameter equal to or smaller than the nominaldiameter of the assembly and then inserting the assembly into aninelastic bushing of a diameter smaller than the nominal outer diameterof the assembly. It is, therefore, not necessary to be concerned withthe tolerances of either the stub shaft, stud, pin, etc. or of thesurrounding bushing. The mounting of the device is relatively simple asalready indicated and it can be dismounted with ease. Upon removal ofthe inner pin, the precompression is relieved and the bearing member cansimply be withdrawn from any retaining bushing and reused elsewhere orintroduced again into a pivot assembly.

We have already noted that the longitudinal slits, which terminate atboth ends of the assembly, may be provided with transversely extendingnarrow connecting webs which interrupt windows and preferably have awidth equal to or less than the width of the wide portion of thewindows. The windows reach over substantially the entire width of thesleeve or shell beyond its end as mentioned earlier and preferablyterminate at least at one end of each window along an edge of thesheet-metal strip which is rolled to form the shell. Wheresingle-opening windows are provided along each generatrix, we prefer toalternate the windows so that the alternate windows have narrow slotportions opening on opposite sides of the sheet metal strip. Withplural-opening windows, however, a narrow slot portion is provided foreach window at each side of the strip. In these systems, an especiallyuniform distribution of stress is obtained and a relatively high degreeof expansion and contraction is made possible and a high degree ofcompression can be generated without overstressing of distorting themetal strip. It will also be apparent that the aforedescribedarrangement provides improved frictional engagement with both the innerpin and the outer sleeve or bushing.

An importnat feature of the present invention is that the width W atleast of the main portion of each window is much greater than thethickness t of the sheetmetal strip from which the sleeve or shell isrolled. In Practice, m e a 3 5! 2d pt fira zlx b tween St and 8 t.Moreover, the slotted metal is so provided with windows that at least 40percent of the area of the sheet-metal shell or strip and preferablymore than 50 percent of the area is formed by these openings. Theserelationships guarantee an effective inner film of elastomer along theinner surface of an inner sheet-metal shell and/or an effective outerfilm along the outer surface of the outer shell, these films orelastomer layers being deflectible through the windows into theelastomer body between the shells upon radial compression. Since theelastomer acts as a confined fluid, the radial stiffness remainsunaltered upon such compression although a more effective journaling ofthe rotatable member is ensured. Here again, the useful life of theelastomer body is increased. Advantageously, the system permits torquetransfer between the inner pin and the outer bushing in a particularlyconvenient manner and without slippage at the interface between theelastomer and the metal shells. The overall stiffness of the system,moreover, is augmented by the presence of elastomer in the windows andby the force absorbed by the system in tending to draw these portions ofthe elastomeric material out of the windows. Finally, we should mentionthat the bearing assemblies of the present invention can be madeinexpensively and simply by the stamping of the parts from sheet metal,thereby controlling the stiffness of the metal shell or sleeve withease. Relatively small bushings and pins may be used with the bearingassemblies of this invention.

DESCRIPTION OF THE DRAWING The above and other objects, features andadvantages of the present invention will become more readily apparentfrom the following description reference being made to the accompanyingdrawing in which:

FIG. 1 is an elevational view, partly broken away, of a cylindricalpivot assembly according to the present invention;

FIG. 2 is a partial axial cross-sectional view through the cylindricalpivot assembly of FIG. 1;

FIG. 3 is an elevational view of the metal sheet adapted to form asleeve for the cylindrical pivot assembly of FIGS. 1 and 2 prior to therolling of the strip into the sleeve configuration and representing,therefore, a partial developed view of the metal sleeve;

FIG. 4 is a view similar to FIG. 3 wherein, however, a different slotarrangement is provided;

FIG. 5 is a cross-sectional view taken along the line VV of FIG. 4;

FIG. 6 is a view similar to FIG. 3 illustrating another embodiment ofthe invention;

FIG. 7 is an axial cross-sectional view through a generally cylindricalpivot or bearing assembly according to the present invention, having anannular radially extending flange at one end thereof;

FIG. 8 is an end view of the assembly of FIG. 7;

FIG. 9 is an enlarged cross-sectional view, in fragmentary form,corresponding to a cross-section along the line IX-IX of FIG. 7;

FIG. 10 is an elevational view of a cylindrical pivot assembly accordingto another feature of the invention, partly broken away and partly shownin axial crosssection;

FIG. 11A is a fragmentary axial cross-sectional view showing anothercylindrical arrangement according to the invention prior to insertioninto its working positron;

FIG. 11B is a view similar to FIG. 11A of the same cylindrical pivotassembly after insertion;

FIG. 12 is an end elevational view, partly in axial cross-section, of aconical pivot assembly according to the invention;

FIG. 13 is an axial cross-sectional view showing still anothercylindrical arrangement in its working position;

FIG. 14 is a view similar to FIG. 13 but illustrating another embodimentof the invention;

FIG. 15 is a fragment of a cross-section taken along the line XV-XV ofFIG. 14 and drawn to an enlarged scale; I

FIG. 16 is a fragmentary axial cross-sectional view through a ball jointembodying the principles of the invention;

FIG. 17 is a view similar to FIG. 16 but illustrating another embodimentof the invention;

FIG. 18 is an elevational view of a portion of the sheet-metal sleevefor a ball joint according to the present invention, prior to shapingand, therefore, in a developed state;

FIG. 19 is a developed view' of a metal strip adapted to be incorporatedinto a conical joint according to the invention and likewiserepresenting this strip in an unrolled state;

FIG. 20 is an axial cross-sectional view through a general conical pivotassembly according to the present invention, the assembly having aradially extending annular flange at the broad base of the frustocone;

FIG. 21 is an end view, partly broken away of the assembly ofFIG. 20;

FIG. 22 is a cross-section taken along the line XXII- XXII of FIG. 20;and

FIG. 23 is a ball joint representing a modification of the system shownin FIG. 20.

SPECIFIC DESCRIPTION In FIGS. 1 and 2, we have shown a pivot assemblyfor an automotive-vehicle steering linkage which comprises an outermetal sleeve 2, an inner metal sleeve 1 and a rubber layer, ring orcylindrical body 3, vulcanized to the metal sleeves. As can be seen fromFIG. 2, the rubber ring 3 not only is vulcanized at the inner surface 3aof the outer ring and the outer surface 3b of the inner ring, but alsohas thin rubber layers 4 and 7 which extend through windows 5 and 6 inthe inner and outer sleeves and are continuous along the outer peripheryand the inner periphery of the assembly. The layers 4 and 7 arerespectively vulcanized to the outer surface of the metal sleeve 2 at 4aand the inner surface of the metal sleeve I at 7a while substantiallycompletely covering these surfaces. The film 7 has been stripped awayfrom the left-hand half of the inner sleeve 1 in FIG. 2 so that thewindows 5 can be seen clearly. Similarly the layer 4 has been strippedaway from the left-hand part of the outer sleeve 2 to reveal the windows6. As is also apparent from FIGS. 1 and 2, the windows 5 and 6 eachconsist of slots opening alternately at opposite end faces of thecylindrical bodies, the windows having relatively large width W over thegreater part of the length L of the respective sleeve but terminatingalternately at opposite ends in small lengths l of narrower portionswith a width w. Advantageously, the ratio W/w ranges between 3:1 andl0:l, the length ratio L/l ranges between 8:1 to 20:1 and the actuallength S 0.7 L to 0.95L. As will be apparent hereinafter, the windowalong arespective generatrix of the sleeve may be subdivided into aplurality of openings having lengths S and preferably totalling S asdefined above. In any event S 2,5 where 2,, represents summation overeach of the openings along a single generatrix and S is at least equalto 0.5 L where L is the generatrix. Furthermore, S may range between 4 Wand 10 W but preferably is between 5 W and 6 W,inclusive.

In FIGS. 3 6, we have shown metal strips according to the inventionprior to rolling. In FIG. 3, the strip 8 has parallel sides 8a and 8b atwhich the windows in the form of slots 9, 10 open in alternatelyopposite directions. Each slot consists of the wide portion 9 mentionedearlier and a narrower portion 10. Narrow webs 11 whose width w =1 serveto hold the strip together.

In the embodiment of FIGS. 41 and 5, the windows are not staggered. Inthis case, each of the windows opens on both sides of the strip-but issubdivided along a generatrix of the eventual cylinder to provideopenings 9' of shorter length S so that webs 12 of metal remain betweenthe two openings of each window. The strip 8 is thus held together bythe webs 12 while the narrow slot portions 10' open at both longitudinaledges 8a and 8b. FIG. 5 shows that the metal strip may be provided withcorrugations or ridges 13 separated by troughs and defining the webs asillustrated. In FIG. 6, the wide portion 9" of each window is providedwith generally triangular portions merging at a broad base andterminating at one end in the narrow slot 10" while the opposite end ofthe window ends close to the longitudinal edge 8b of the metal strip 8but defines the connecting web 11 therewith. In the embodiments of FIGS.3 and 4, the wide portions of the windows have parallel sides.

In FIGS. 7 9, we have shown a bearing system adapted to be used in placeof the ball joint in a steering linkage wherein an inner metal sleeve 14is provided with slots 15 as described in connection with FIG. 3 and issurrounded by a body 16 of elastomeric material vulcanized to thesheet-metal sleeve. As is apparent from FIGS. 8 and 9, the windows 15 ofthe sheet-metal sleeve 14 are spaced apart by narrow webs 14a of thesheet-metal material, the webs 14a having a transverse width C (see FIG.3) which at most is equal to the width W. This relationship can best beseen in FIG. 9 from which it is apparent that the elastomeric material16 includes a ligature 16a filling each window 15 and unitarily bondedto the layer 22 of the elastomer which lines and is bonded to the innersurface of the metal sleeve 14. The elastomeric body 16, which is moldedto form a flange I7 unitary with the other portions of the elastomersleeve, is provided with a metal ring 21 which is likewise slotted toallow an elastomer layer 16 to form along the right-hand or outer faceof the ring 21. The ring 20 along the back of the flange is likewiseslotted to permit the layer 18 of elastomer to form on its face.

As can be seen in FIG. 8, the slots a in the rings 20 and 21 may havethe same configuration as described in connection with FIG. 3.

A modification of the system is illustrated in FIG. 10 wherein the innersheet-metal shell 23a is provided with only a single throughgoing slot23, e.g. formed by rolling an unperforated strip of sheet metal so thatthe juxtaposed ends do not touch. An elastomer body 26 is vulcanized tothe outer surface of the sleeve 23a which may be coated internally withan elastomer layer 23b, while a slotted shell 24 is provided along theexterior of the elastomer body 26 and is formed with slots as describedin connection with FIG. 3. The outer elastomer layer 27 is vulcanized tothe outer surface of sleeve 24 and through the windows 25 thereof to theinner layer 26. The right-hand side of FIG. 10 shows the sleeve 24 inelevation with the elastomer layer cut away so that the windows 25 willbe more readily apparent. In this embodiment as well, it is apparentthat ligatures of elastomeric material bond the elastomer layerstogether.

In FIG. 11A, we have shown an arrangement which is generally similar tothat of FIG. 2, i.e. a system in which an outer slotted cylindricalsleeve 30 and an inner slotted cylindrical sleeve 28 sandwich anelastomer layer 31 between them. The elastomer layer 31 is, of course,vulcanized to the slotted metal sleeves which are of the configurationdescribed in connection with FIG. 3, and is unitary with inner and outerrubber layers 32 and 33 connected to the main rubber body through thewindows 29 of the metal shells. In this embodiment, the stud 34 is shownto be inserted into the interior of the assembly which is not materiallycompressed thereby. Thereafter, the entire assembly is inserted into asleeve 35 (FIG. 11B) whose inner diameter is smaller than the nominalouter diameter of the bearing such that the elastomer layer 31a iscompressed between the stud 34 and the bushing 35. The body 31a ofelastomeric material thus can be considered under prestress.

Another arrangement has been shown in FIG. 12 wherein a conical metalbody 36 having a threaded bore 36a adapted to receive a bolt formingpart of a pivot system for an automotive steering linkage (see pages 402ff. of PRINCIPLES OF AUTOMOTIVE VE- HICLES, U.S. Government PrintingOffice, Washington,D.C. 1956), is bonded by vulcanization to thefrustoconical body 38 of elastomeric material. A metal shell 37 whosegeneratrices run parallel to those of the frustoconicl surface of member36, is provided with windows 39 as previously described and isvulcanized to the elastomeric material 38, a portion of which forms alayer 38a along the exterior of the shell 37. It should be understoodthat the assembly of FIG. 12 is stressed by inserting the assembly intosleeve or cup whose conicity (conical half angle) is the same as that ofshell 37 but which has a diameter less than that of this shell wherebythe body of the elastomer 38 is compressed. In all of the embodimentsdescribed, the outer or bushing member can rotate while the inner orstud member remains fixed or vice versa. Both can be movable relative tosome third element and inevitably some lateral or radial displacementmay be encountered. In the case of the arrangement of FIG. 12, the innermember 36 may twist to a greater or lesser extent in the direction ofarrow A in an axial plane through the assembly. The yieldable joint ofthe present invention, however, permits such movement with three degreesof freedom, with the limtations provided by the elasticity of theelastomeric material.

Still another embodiment of the invention has been illustrated in FIG.13 wherein the shaft 43 is provided with an outer sleeve 44 of alow-friction synthetic resin, e.g. polytetrafluoroethylene, enabling theshaft to re tate with respect to the outer member or bushing 49. Thebearing assembly is first thrust over the shaft 43 and then passed intothe bushing 49. The slots or windows 48 in the sheet-metal outer shell46 are thereby compressed circumferentially and the elastomer layer 40vulcanized to this metal shell is radially compressed. The outer layer47 of elastomer which passes through the windows 48 and forms a layeralong the exterior of the assembly, is snugly received in the bushing49. This layer 47 provides frictional retention of the bearing as theshaft 43 rotates.

The sleeve 44 is provided, as is best seen in FIG. 14, withlongitudinally extending grooves 45 (see also FIG. 15) which can containa lubricant. An inner sleeve 50 may be interposed between the elastomerlayer 40 and the plastic sleeve 44 as also has been illustrated in FIG.14. In both of the embodiments (FIGS. 13 and 14), the elastomeric bodyis provided with sealing lips 41 at its opposite extremities projectingbeyond the sleeves and held by a respective compression ring 42 againstthe shaft. The rings 42 provide a generally radially inward bias tocause the lips 41 to hug the shaft as indicated.

In the embodiment of FIG. 17, the elastomeric body 55, composed ofnatural or synthetic rubber, is sandwiched between a pair of metalshells 53 and 54 bent from flat annular disks as shown in FIG. 18. BothFIG. 16 and FIG. 17 show ball joints in which the male member 51 isreceived within the bearing assembly of the present invention while aball-shaped cap 52 is mounted thereon. The elastomeric layers shown at 4and 7, for example, in FIG. 2 likewise have their counterpartsin layerslocated between member 51 and shell 53 and between shell 54 and member52 respectively. The ball joints in the position illustrated in FIGS. 16and 17, moreover, are adapted to carry a vertical load continuouslyapplied from above and may form the retary bearing ofa freight car pivotor king pin. The load continuously applied from above forms theprecompressive stress. The embodiment of FIG. 17 makes use of a singlemetal shell 56 sandwiched elastomeric layers which are vulcanizedthereto, the shells being slotted as previously described. In FIG. 18,the slot arrangement of the shells is shown in greater detail. Thus theslots 60 may lie along respective generatrices and can be separated by anarrow web 59 analogous to the web 12 previously described. In theflattened position of the disk from which the shell is bent, thesegeneratrices correspond to radii. The large-width slots 60 comprise wideportions 60a and narrow portions 60b, the latter terminating at theperiphery of the disk. Between these double-opening windows, there maybe provided further windows 61 which reduce the inter-window spacing butneed not extend the full generatrix-Iength of the member. Of course,when the disk is bent into the spheroidal configuration shown at 53, 54or 56, the windows may permit ligatures of the rubber (from layer or thelayers 57 and 58) to pass therethrough. It has been found to beadvantageous, in this connection, to leave at least some of the windowsfree and provide a lubricant therein (this system may be used as wellwith the embodiments previously described). The elastomer bodies 55, 57and 58 are secured to the metal shells 53, 54 and 56 by vulcanization. y

In FIG. 19, we have shown a strip of metal 62 in which the slotsconverge inwardly from opposite longitudinal edges of the strip therebyfacilitating a bending of the strip into a conical or ballconfiguration. The slots 63 and 64 may be aligned along generatrices ofthe bent member. The windows, slots etc. are preferably produced bystamping and the shells can be shaped by stamping or rolling. Preferablythe slots 63 along one side are shorter than the slots 64 along theother to facilitate bending into a spheroidal configuration.

In FIGS. 22, we have shown yet another embodiment of the inventionwherein a cylindrical pin can be accommodated while a conical sleeve maysurround the bearing or the latter can be mounted by its flange. In thisembodiment, the frustoconical tubular elastomer body 66 has a metallicshell 67 vulcanized to it and embedded therein. The shell is composed ofsheet metal but, like the shells previously described, may be composedofflexible synthetic resin as well. The shell 67 is rolled from stampedsheet metal and is provided with slots, e.g. a single slot at which theends of the sheet-metal strip are juxtaposed as shown at 68, this slothaving a width which is several times the thickness of the sheet metal.The shell is perforated at 69 and is covered over its unperforatedportions of the inner surface with an elastomeric film 70 as previouslydescribed. The annular flange 65 is provided along its opposite axialsurfaces with metal rings 71 and 72 which are also perforated, theperforations being circular holes. The outer surfaces of these rings arecovered with elastomeric linings 73 and 74. The flange 65 also hasembedded therein an intermediate ring 75 which likewise is perforated.The rubber layers 70, 73 and 74 are produced by penetration of theelastomeric mass through the holes 69 and constitute a uniform film.

In FIGS. 23, there is shown a ball joint for a steering linkage having aball-shaped support 76 provided with eyes 77 and 78 for anchoring bolts.The bearing is in this case formed as two half bearings of generallyhemispherical configuration (79,80) which are disposed symmetricallyupon the body 76. The hemispherical rubber bodies 81 and 82 arevulcanized to outer metal shells 83 and 84 which are provided with edgeflanges 85 and 86. Metallic inner shells 87 and 88 are also vulcanizedto the rubber body and have a spherical configuration complementary tothat of body 76. The shells are provided with perforations as shown at69 as well as with slots as represented at 89. A clamping sleeve 91 inthe form of a cylindrical housing is pressed over the bearing membersand has a shoulder against which the outer flange 90 is held when aspring ring 93 is inserted into a recess at the other axial opposite endof the sleeve 91 to bear against the flange 92.

The exterior of the inner shells 87, 88 can be provided with a film-likerubber layer 70 as is the case in FIGS. 20 22 or with a synthetic-resincoating of low coefficient of friction by an adhesive or by braking. Theshaft is thus able to move with a minimum of frictional impediment assoon as the restoring force of the rubber is greater than the frictionforce in the contacting surfaces of the shaft. With small deformations,only the usual molecular displacement within the rubber body occurs. Theslotted arrangement of the shells ensures a uniform distribution ofpressure upon the inner member.

We claim:

1. A joint assembly, especially for the steering linkage of anautomotive vehicle, comprising an annular elastomeric body having aconfiguration conforming to a surface of revolution; and at least onethin-wall shell conforming to said surface of revolution and vulcanizedto said annular elastomeric body and provided with a plurality ofelongated slots spanning said shell along generatrices thereof from endto end, a multiplicity of elongated slots being provided in said shellin angularly spaced relationship along respective generatrices andextending substantially from one side of said shell to the opposite sidethereof.

2. The assembly defined in claim 1 wherein said slots terminatealternately at opposite ends of said shell.

3. The assembly defined in claim 1 wherein said shell is a rolledslotted sheet metal strip.

4. The assembly defined in claim I wherein said annular elastomeric bodyis disposed along one side of said shell, further comprising a secondelastomeric body disposed along an opposite side of said shell andvulcanized thereto.

5. The assembly defined in claim 1 wherein the elastomeric material ofsaid body is formed on opposite sides of said shell and is vulcanizedthereto, at least some of said slots being free from elastomericmaterial and being filled with a lubricant.

6. The assembly defined in claim 1, further comprising a pin received inand spreading said shell.

7. The assembly defined in claim 1, further comprising a bushingreceiving said shell and said elastomeric body and compressing thelatter.

8. The assembly defined in claim 1 wherein said elastomeric body andsaid shell are of generally spheroidal configuration, said shell beingshaped from a piece of slotted flat sheet metal.

9. The assembly defined in claim 1 wherein slotted inner and outersheet-metal shells are vulcanized to said elastomeric body on oppositesides thereof, said shells including an inner shell and an outer shell,said assembly further comprising a respective elastomeric layerinternally lining said inner shell and externally lining said outershell.

10. The assembly defined in claim 9 wherein said slots have widthssubstantially larger than the thickness of the sheet metal of theshells.

11. The assembly defined in claim 1 wherein said elastomeric body andsaid shell are generally hemispherical, said assembly further comprisinga ball member received in said elastomeric body and said shell and afurther similar body of elastomeric material and shell surrounding saidball member and connected to the first-mentioned body and shell.

12. The assembly defined in claim 11, further comprising means forradially and axially compressing said bodies against said ball member.

13. The assembly defined in claim 1, further comprising a sleeve of alow-friction synthetic resin received in said elastomeric body and saidshell and adapted to accommodate a shaft.

141. A joint assembly, especially for the steering linkage of anautomotive vehicle, comprising an annular elastomeric body having aconfiguration conforming to a surface of revolution; and at least onethin-wall shell conforming to said surface of revolution and vulcanizedto said annular elastomeric body and provided with a plurality ofelongated slots spanning said shell along generatrices thereof from endto end, said slots forming windows extending over a major portion of thelength of the respective generatrix, said shell being provided withnarrow webs terminating said windows and holding said shell together.

15. The assembly defined in claim 14 wherein said slots terminatealternately at opposite ends of said shell.

16. The assembly defined in claim 14 wherein said shell is a rolledslotted sheet metal strip.

17. The assembly defined in claim 14 wherein said slots are formed overthe major portion of their lengths as relatively wide windows, each ofsaid slots having a narrow slot portion leading from the respectivewindows to one of said ends.

18. The assembly defined in claim 17 wherein each of said windowsconsists of a plurality of openings spaced apart along a respectivegeneratrix by a web, said webs having a corrugated configuration.

19. The assembly defined in claim 14 wherein said annular elastomericbody is disposed along one side of said shell, further comprising asecond elastomeric body disposed along an opposite side of said shelland vulcanized thereto.

20. The assembly defined in claim 14 wherein the elastomeric material ofsaid body is formed on opposite sides of said shell and is vulcanizedthereto, at least some of said slots being free from elastomericmaterial and being filled with a lubricant.

21. The assembly defined in claim 14, further comprising a pin receivedin and spreading said shell.

22. The assembly defined in claim 14, further comprising a bushingreceiving said shell and said elastomeric body and compressing thelatter.

23. The assembly defined in claim 14 wherein said elastomeric body andsaid shell are of generally spheroidal configuration, said shell beingshaped from a piece of slotted flat sheet metal.

24. The assembly defined in claim 14 wherein slotted inner and outersheet-metal shells are vulcanized to said elastomeric body on oppositesides thereof, said shells including an inner shell and an outer shell,said assembly further comprising a respective elastomeric layerinternally lining said inner shell and externally lining said outershell.

25. The assembly defined in claim 24 wherein said slots have widthssubstantially larger than the thickness of the sheet metal of theshells.

26. The assembly defined in claim 14 wherein said elastomeric body isprovided with a circumferential radially extending flange at one endthereof, said assembly further comprising annular metal ringssandwiching said flange between them and vulcanized to the flange, saidrings being coated with layers of elastomeric material.

27. The assembly defined in claim 14 wherein said elastomeric body andsaid shell are generally hemispherical, said assembly further comprisinga ball member received in said elastomeric body and said shell and afurther similar body of elastomeric material and shell surroundingsaidball member and connected to the first-mentioned body and shell.

28. The assembly defined in claim 27, further comprising means forradially and axially compressing said bodies against said ball member.

29. The assembly defined in claim 14, further comprising a sleeve of alow'friction synthetic resin received in said elastomeric body and saidshell and adapted to accommodate a shaft.

30. A joint assembly, especially for the steering linkage of anautomotive vehicle, comprising an annular elastomeric body having aconfiguration conforming to a surface of revolution; and at least onethin-wall shell conforming to said surface of revolution and vulcanizedto said annular elastomeric body and provided with a plurality ofelongated slots spanning said shell along generatrices thereof from endto end, said slots being formed over the major portion of their lengthsas relatively wide windows, each of said slots having a narrow slotportion leading from the respective windows to one of said ends.

31. The assembly defined in claim 30 wherein each of said windowsconsists of a plurality of openings spaced apart along a respectivegeneratrix by a web, said webs having a corrugated configuration.

32. The assembly defined in claim 30 wherein said slots terminatealternately at opposite ends of said shell.

33. The assembly defined in claim 30 wherein said shell is a rolledslotted sheet metal strip.

34. The assembly defined in claim 30 wherein said annular elastomericbody is disposed along one side of said shell.

35. The assembly defined in claim 30 wherein the elastomeric material ofsaid body is formed on opposite sides of said shell and is vulcanizedthereto, at least some of said slots being free from elastomericmaterial and being filled with a lubricant.

36. The assembly defined in claim 30, further comprising a pin receivedin and spreading said shell.

37. The assemlby defined in claim 30, further comprising a bushingreceiving said shell and said elastomeric body and compressing thelatter.

38. The assembly defined in claim 30 wherein said elastomeric body andsaid shell are of generally spheroidal configuration, said shell beingshaped from a piece of slotted flat sheet metal.

39. The assembly defined in claim 30 wherein slotted inner and outersheet-metal shells are vulcanized to said elastomeric body on oppositesides thereof, said shells including an inner shell and an outer shell,said assembly further comprising a respective elastomeric layerinternally lining said inner shell and externally lining said outershell.

40. The assembly defined in claim 39 wherein said slots have widthssubstantially larger than the thickness of the sheet metal of theshells.

41. The assembly defined in claim 30 wherein said elastomeric body isprovided with a circumferential radially extending flange at one endthereof, said assembly further comprising annular metal ringssandwiching said flange between them and vulcanized to the flange, saidrings being coated with layers of elastomeric material.

42. The assembly defined in claim 30 wherein said elastomeric body andsaid shell are generally hemispherical, said assembly further comprisinga ball member received in said elastomeric body and said shell and afurther similar body of elastomeric material and shell surrounding saidball member and connected to the first-mentioned body and shell.

43. The assembly defined in claim 42, further comprising means forradially and axially compressing said bodies against said ball member.

44. The assembly defined in claim 30, further comprising a sleeve of alow-friction synthetic resin received in said elastomeric body and saidsheel and adapted to accommodate a shaft.

45. A joint assembly, especially for the steering linkage of anautomotive vehicle, comprising an annular elastomeric body having aconfiguration conforming to a surface of revolution; and at least onethin-wall shell conforming to said surface of revolution and vulcanizedto said annular elastomeric body and provided with at least oneelongated slot spanning said shell along generatrices thereof from endto end, said elastomeric body being provided with a circumferentialradially extendin flange at one end thereof, said assembly furthercomprising annular metal rings sandwiching said flange between them andvulcanized to the flange, said rings being coated with layers ofelastomeric material.

46. A joint assembly as defined in claim 45 wherein a multiplicity ofelongated slots is provided in said shell in angularly spacedrelationship.

47. The assembly defined in claim 46 wherein said slots terminatealternately at opposite ends of said shell.

48. The assembly defined in claim 46 wherein said shell is a rolledslotted sheet metal strip.

49. The assembly defined in claim 46 wherein said slots are formed overthe major portion of their lengths as relatively wide windows, each ofsaid slots having a narrow slot portion leading from the respectivewindows to one of said ends.

50. The assembly defined in claim 49 wherein each of said windowsconsists of a plurality of openings spaced apart along a respectivegeneratrix by a web, said webs having a corrugated configuration.

51. The assembly defined in claim 46 wherein saidannular elastomericbody is disposed along one side of said shell, further comprising asecond elastomeric body disposed along an opposite side of said shelland vulcanized thereto.

52. The assembly defined in claim 46 whrein the elastomeric material ofsaid body is formed on opposite sides of said shell and is vulcanizedthereto, at least some of said slots being free from elastomericmaterial and being filled with a lubricant.

S3. The assembly defined in claim 46, further comprising a pin receivedin and spreading said shell.

54. The assembly defined in claim 46, further comprising a bushingreceiving said shell and said elastomeric body an compressing thelatter.

55. The assembly defined in claim 46 wherein said elastomeric body andsaid shell are of generally spheroidal configuration, said shell beingshaped from a piece of slotted flat sheet metal.

56. The assembly defined in claim 46 wherein slotted inner and outersheet-metal shells are vulanized to said elastomeric body on oppositesides thereof, said shells including an inner shell and an outer shell,said assembly further comprising a respective elastomeric layerinternally lining said inner shell and externally lining said outershell.

57. The assembly defined in claim 56 wherein said slots have widthssubstantially larger than the thickness of the sheet metal of theshells.

58. The assembly defined in claim 56 wherein said elastomeric body andsaid shell are generally hemispherical, said assembly further comprisinga ball member received in said elastomeric body and said shell and afurther similar body of elastomeric material and shell surrounding saidball member and connected to the first-mentioned body and shell.

59. The assembly defined in claim 58, further comprising means forradially and axially compressing said bodies against said ball member.

60. The assembly defined in claim 46, further comprising a sleeve oflow-friction synthetic resin received in said elastomeric body and saidshell and adapted to accommodate a shaft.

1. A joint assembly, especially for the steering linkage of anautomotive vehicle, comprising an annular elastomeric body having aconfiguration conforming to a surface of revolution; and at least onethin-wall shell conforming to said surface of revolution and vulcanizedto said annular elastomeric body and provided with a plurality ofelongated slots spanning said shell along generatrices thereof from endto end, a multiplicity of elongated slots being provided in said shellin angularly spaced relationship along respective generatrices andextending substantially from one side of said shell to the opposite sidethereof.
 2. The assembly defined in claim 1 wherein said slots terminatealternately at opposite ends of said shell.
 3. The assembly defined inclaim 1 wherein said shell is a rolled slotted sheet metal strip.
 4. Theassembly defined in claim 1 wherein said annular elastomeric body isdisposed along one side of said shell, further comprising a secondelastomeric body disposed along an opposite side of said shell andvulcanized thereto.
 5. The assembly defined in claim 1 wherein theelastomeric material of said body is formed on opposite sides of saidshell and is vulcanized thereto, at least some of said slots being freefrom elastomeric material and being filled with a lubricant.
 6. Theassembly defined in claim 1, further comprising a pin received in andspreading said shell.
 7. The assembly defined in claim 1, furthercomprising a bushing receiving said shell and said elastomeric body andcompressing the latter.
 8. The assembly defined in claim 1 wherein saidelastomeric body and said shell are of generally spheroidalconfiguration, said shell being shaped from a piece of slotted flatsheet metal.
 9. The assembly defined in claim 1 wherein slotted innerand outer sheet-metal shells are vulcanized to said elastomeric body onopposite sides thereof, said shells including an inner shell and anouter shell, said assembly further comprising a respective elastomericlayer internally lining said inner shell and externally lining saidouter shell.
 10. The assembly defined in claim 9 wherein said slots havewidths substantially larger than the thickness of the sheet metal of theshells.
 11. The assembly defined in claim 1 wherein said elastomericbody and said shell are generally hemispherical, said assembly furthercomprising a ball member received in said elastomeric body and saidshell and a further similar body of elastomeric material and shellsurrounding said ball member and connected to the first-mentioned bodyand shell.
 12. The assembly defined in claim 11, further comprisingmeans for radially and axially compressing said bodies against said ballmember.
 13. The assembly defined in claim 1, further comprising a sleeveof a low-friction synthetic resin received in said elastomeric body andsaid shell and adapted to accommodate a shaft.
 14. A joint assembly,especially for the steering linkage of an automotive vehicle, comprisingan annular elastomeric body having a configuration conforming to asurface of revolution; and at least one thin-wall shelL conforming tosaid surface of revolution and vulcanized to said annular elastomericbody and provided with a plurality of elongated slots spanning saidshell along generatrices thereof from end to end, said slots formingwindows extending over a major portion of the length of the respectivegeneratrix, said shell being provided with narrow webs terminating saidwindows and holding said shell together.
 15. The assembly defined inclaim 14 wherein said slots terminate alternately at opposite ends ofsaid shell.
 16. The assembly defined in claim 14 wherein said shell is arolled slotted sheet metal strip.
 17. The assembly defined in claim 14wherein said slots are formed over the major portion of their lengths asrelatively wide windows, each of said slots having a narrow slot portionleading from the respective windows to one of said ends.
 18. Theassembly defined in claim 17 wherein each of said windows consists of aplurality of openings spaced apart along a respective generatrix by aweb, said webs having a corrugated configuration.
 19. The assemblydefined in claim 14 wherein said annular elastomeric body is disposedalong one side of said shell, further comprising a second elastomericbody disposed along an opposite side of said shell and vulcanizedthereto.
 20. The assembly defined in claim 14 wherein the elastomericmaterial of said body is formed on opposite sides of said shell and isvulcanized thereto, at least some of said slots being free fromelastomeric material and being filled with a lubricant.
 21. The assemblydefined in claim 14, further comprising a pin received in and spreadingsaid shell.
 22. The assembly defined in claim 14, further comprising abushing receiving said shell and said elastomeric body and compressingthe latter.
 23. The assembly defined in claim 14 wherein saidelastomeric body and said shell are of generally spheroidalconfiguration, said shell being shaped from a piece of slotted flatsheet metal.
 24. The assembly defined in claim 14 wherein slotted innerand outer sheet-metal shells are vulcanized to said elastomeric body onopposite sides thereof, said shells including an inner shell and anouter shell, said assembly further comprising a respective elastomericlayer internally lining said inner shell and externally lining saidouter shell.
 25. The assembly defined in claim 24 wherein said slotshave widths substantially larger than the thickness of the sheet metalof the shells.
 26. The assembly defined in claim 14 wherein saidelastomeric body is provided with a circumferential radially extendingflange at one end thereof, said assembly further comprising annularmetal rings sandwiching said flange between them and vulcanized to theflange, said rings being coated with layers of elastomeric material. 27.The assembly defined in claim 14 wherein said elastomeric body and saidshell are generally hemispherical, said assembly further comprising aball member received in said elastomeric body and said shell and afurther similar body of elastomeric material and shell surrounding saidball member and connected to the first-mentioned body and shell.
 28. Theassembly defined in claim 27, further comprising means for radially andaxially compressing said bodies against said ball member.
 29. Theassembly defined in claim 14, further comprising a sleeve of alow-friction synthetic resin received in said elastomeric body and saidshell and adapted to accommodate a shaft.
 30. A joint assembly,especially for the steering linkage of an automotive vehicle, comprisingan annular elastomeric body having a configuration conforming to asurface of revolution; and at least one thin-wall shell conforming tosaid surface of revolution and vulcanized to said annular elastomericbody and provided with a plurality of elongated slots spanning saidshell along generatrices thereof from end to end, said slots beingformed over the major portion of their lengths as relatively widewindows, each of said slots havinG a narrow slot portion leading fromthe respective windows to one of said ends.
 31. The assembly defined inclaim 30 wherein each of said windows consists of a plurality ofopenings spaced apart along a respective generatrix by a web, said webshaving a corrugated configuration.
 32. The assembly defined in claim 30wherein said slots terminate alternately at opposite ends of said shell.33. The assembly defined in claim 30 wherein said shell is a rolledslotted sheet metal strip.
 34. The assembly defined in claim 30 whereinsaid annular elastomeric body is disposed along one side of said shell.35. The assembly defined in claim 30 wherein the elastomeric material ofsaid body is formed on opposite sides of said shell and is vulcanizedthereto, at least some of said slots being free from elastomericmaterial and being filled with a lubricant.
 36. The assembly defined inclaim 30, further comprising a pin received in and spreading said shell.37. The assemlby defined in claim 30, further comprising a bushingreceiving said shell and said elastomeric body and compressing thelatter.
 38. The assembly defined in claim 30 wherein said elastomericbody and said shell are of generally spheroidal configuration, saidshell being shaped from a piece of slotted flat sheet metal.
 39. Theassembly defined in claim 30 wherein slotted inner and outer sheet-metalshells are vulcanized to said elastomeric body on opposite sidesthereof, said shells including an inner shell and an outer shell, saidassembly further comprising a respective elastomeric layer internallylining said inner shell and externally lining said outer shell.
 40. Theassembly defined in claim 39 wherein said slots have widthssubstantially larger than the thickness of the sheet metal of theshells.
 41. The assembly defined in claim 30 wherein said elastomericbody is provided with a circumferential radially extending flange at oneend thereof, said assembly further comprising annular metal ringssandwiching said flange between them and vulcanized to the flange, saidrings being coated with layers of elastomeric material.
 42. The assemblydefined in claim 30 wherein said elastomeric body and said shell aregenerally hemispherical, said assembly further comprising a ball memberreceived in said elastomeric body and said shell and a further similarbody of elastomeric material and shell surrounding said ball member andconnected to the first-mentioned body and shell.
 43. The assemblydefined in claim 42, further comprising means for radially and axiallycompressing said bodies against said ball member.
 44. The assemblydefined in claim 30, further comprising a sleeve of a low-frictionsynthetic resin received in said elastomeric body and said sheel andadapted to accommodate a shaft.
 45. A joint assembly, especially for thesteering linkage of an automotive vehicle, comprising an annularelastomeric body having a configuration conforming to a surface ofrevolution; and at least one thin-wall shell conforming to said surfaceof revolution and vulcanized to said annular elastomeric body andprovided with at least one elongated slot spanning said shell alonggeneratrices thereof from end to end, said elastomeric body beingprovided with a circumferential radially extendin flange at one endthereof, said assembly further comprising annular metal ringssandwiching said flange between them and vulcanized to the flange, saidrings being coated with layers of elastomeric material.
 46. A jointassembly as defined in claim 45 wherein a multiplicity of elongatedslots is provided in said shell in angularly spaced relationship. 47.The assembly defined in claim 46 wherein said slots terminatealternately at opposite ends of said shell.
 48. The assembly defined inclaim 46 wherein said shell is a rolled slotted sheet metal strip. 49.The assembly defined in claim 46 wherein said slots are formed over themajor portion of their lengths as relatively wide windows, each Of saidslots having a narrow slot portion leading from the respective windowsto one of said ends.
 50. The assembly defined in claim 49 wherein eachof said windows consists of a plurality of openings spaced apart along arespective generatrix by a web, said webs having a corrugatedconfiguration.
 51. The assembly defined in claim 46 wherein said annularelastomeric body is disposed along one side of said shell, furthercomprising a second elastomeric body disposed along an opposite side ofsaid shell and vulcanized thereto.
 52. The assembly defined in claim 46whrein the elastomeric material of said body is formed on opposite sidesof said shell and is vulcanized thereto, at least some of said slotsbeing free from elastomeric material and being filled with a lubricant.53. The assembly defined in claim 46, further comprising a pin receivedin and spreading said shell.
 54. The assembly defined in claim 46,further comprising a bushing receiving said shell and said elastomericbody an compressing the latter.
 55. The assembly defined in claim 46wherein said elastomeric body and said shell are of generally spheroidalconfiguration, said shell being shaped from a piece of slotted flatsheet metal.
 56. The assembly defined in claim 46 wherein slotted innerand outer sheet-metal shells are vulanized to said elastomeric body onopposite sides thereof, said shells including an inner shell and anouter shell, said assembly further comprising a respective elastomericlayer internally lining said inner shell and externally lining saidouter shell.
 57. The assembly defined in claim 56 wherein said slotshave widths substantially larger than the thickness of the sheet metalof the shells.
 58. The assembly defined in claim 56 wherein saidelastomeric body and said shell are generally hemispherical, saidassembly further comprising a ball member received in said elastomericbody and said shell and a further similar body of elastomeric materialand shell surrounding said ball member and connected to thefirst-mentioned body and shell.
 59. The assembly defined in claim 58,further comprising means for radially and axially compressing saidbodies against said ball member.
 60. The assembly defined in claim 46,further comprising a sleeve of low-friction synthetic resin received insaid elastomeric body and said shell and adapted to accommodate a shaft.